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(No Model.) 8 Sheets-Sheet 2. A. E. CUTLER & R. DONKIN. HYDRAULICGOMPENSATING PUMP OR ENGINE.

No. 569,091. Patented Oct. 6,1896.

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(No Model.) 8 Sheats'-8heet 3.

A. B..OUTLER & R. DONKIN. HYDRAULIG comrnusnme PUMP 0R ENGINE.

No. 569,091. Patented Oct. 6, 1896.

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(Nb Model.)

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Patented Oct. 6,1896.

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(No Model.) v Sheets-Sheet 5.

A; E. CUTLER 8: R. DONKIN. HYDRAULIC GOMPIINSATING PUMP 0R ENGINE.

PatentedlOotQG, 1896.

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(No Model.) 8 Sheets Sheet 6. A. B. CUTLER & R. DONKIN. HYDRAULICGQMPENSATING PUMP 0R ENGINE. No. 569,091.

BatentedOotiG, 1896.

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I -s Sheets-sheaf 7. A. E-CUTLER & R. DONKIN. HYDRAULIC GOM'PENSATINGPUMP 0R ENGINE.

(No Model.)

Patented Oct. 6; 1896.

UNITED STATES PATE T Orrion.

ARTHUR EDiVARD CUTLER AND REGINALD DONKIN, OF MOSMAN, NEWV SOUTH WALES.

HYDRAULIC COMPENSATING PUMP OR ENGINE.

SPECIFICATION forming part of Letters Patent No. 569,091, dated October6, 1896.

Application filed January 26,1895. Serial No. 536,861. (No model.)

To all whom it may concern.-

Be it known that we, ARTHUR EDWARD CUTLER and REGINALD DONKIN,engineers, subjects of the Queen of Great Britain, residing at Mosman,near Sydney, in the British Colony of New South \Vales, have inventednew and useful Improvements in Hydraulic Compensating Pumps or Enginesand in Devices for Regulating Same, of which the following is aspecification.

This invention relates to improvements in hydraulic compensating pumpsand engines and in devices for regulating same, whereby the amount ofpower expended in such a pump or engine in performing work of varyingextent or degree will be compensated or regulated by the requirements ofthe work to be done, or, in other words, the expenditure of power inraising loads of varying weights will be compensated or regulated in theratio of said weights, and, further, where the work done is of anegative quantity, as where a load is lowered, the reservoir of powerwill be augmented in the ratio of the weight of said'lowering load. Thisinvention is specially serviceable for regulating the quantity of waterused in hydraulic rotary engines, cranes, hoists, elevators, inclinedtramways, and the like, according to the amount of work to be done inraising and lowering varying loads.

An improved hydraulic compensating engine or pump constructed accordingto this invention has a crank-pin which is held in the compensatoryposition in a radial slot in a disk or crank by means of hydraulic pressure acting upon a non-compressible fluid in a doubleended cylinder setradially in or forming part of the crank or crank-disk and whose ram isa double-ended extension of the crank-pin. The ends of this double-endedram cylinder are connected through the crank-shaft and a stationary plugin the end of said crank-shaft to regulating devices, which are adaptedto be operated by hand or automatically, according to the work to bedone or the varying resistance of the load. The position of thecrank-pin being thus alterable in the radial slot of the crank-disk orcrank, either manually or automatically,

the leverage of the crank is adjusted to the load. I The regulatingdevices for the supply and exhaust ofpower from the double-endedram-cylinder of the crank or crank-disk may take the form of a cataractor other hydraulic governor, by means of which a variation of pressurein the main cylinder will cause the desired alteration ofcrank-leverage, though, preferably, these devices would be of one orother of the improved constructions hereinafter described.

In order that this invention may be clearly understood, reference willnow be made to the drawings herewith, in which- Figure 1 is an elevationof a hydraulic engine (usable also as a hydraulic pump) constructedaccording to this invention, and Fig.2 is a central sectional elevationof same. Fig. 3 is a central sectional elevation of regulating device orgovernor for an engine or pump such. as that shown in Figs. 1 and 2, andFig. 4 is a sectional elevation of a fluid-supply vessel or intensifierfor use in connection with such regulating devices. Figs. 5 and 6 areelevations, partly in section and plan, respectively, of a hydraulicpump having an adjustable crank-pin which is automatically controlled bydevices in connection with the ram of a multiplying hydraulic lift. Fig.7 is a partial sectional elevation of the cylinder end of a multiplyinghydraulic lift or hoist or crane having attached thereto devices forregulating a hydraulic compensating pump from same. and side elevationof a modified construction of Fig. 7 and Fig. 10 is a section throughthe turbine, the valve of, and the ram above the head of the valve L andFig. 11 is an enlarged detail, partly in section, of parts of Figs. 8and 9. Figs. 12, 13, and 14. are sections and elevation of an auxiliaryvalve used in the regulating devices, and Figs. 15 to 22 Figs. 8 and 9are front elevation are diagrammatic views of combination andarrangements of elevator-regulating devices and compensating hydraulicpump.

Referring to Figs. 1 and 2, A are the hydraulic cylinders with necessaryvalves, &c., as well understood, and B are the connectingrods to thecrank-pin O in or on disk D on end of crank-shaft E, running in bearingsE, the whole having an appropriate framing. The crank-pin 0 extendsradially in reference the incompressible fluid.

to crank-disk D outwardly and inwardly and takes the form of rams 0,Working in cylinders D in or on disk D, in which at the front ends ofsaid cylinders is a slot D To the back ends of cylinders D the pipes Dand D communicate from separate ports or passages D and D that extendlongitudinally through the shaft E. These ports or passages communicatewith ports or grooves F and F in or on stationary plug F, which is heldon the end of the shaft E by stuffing-box E and gland E and is supportedby a bracketarm E to the outside of which are led the feed and exhaustpipes F and F which are continued in the plug F as ports or passages Fand F The pipe F, passage F port F passage D and pipe D alwaysconstitute a through passage, while at the same time do also pipe Dpassage D, port F, passage F and pipe F the one end of suchcommunications being the back of one of the disk cylinders D and theother end being the ends of regulating-cylinders, as in a cataract orother regulating devices or ports of such devices. The pinion G on theshaft E (shown in gear with wheel G) is for transmitting the power to ahoist, &c., as well understood.

The crank-cylinders D and the passages and pipes connecting with sameare filled completely with some incompressible fluid, preferably withheavy oil, so that pressure exerted in the regulating cylinders ordevices will be transmitted to the rams O and the crank-pin O adjustedat any point in its possible movement in slot D The regulating device(shown in Fig. 3) consists of cylinders H, connected-firmly together byappropriate framing H. In these cylinders H are rams or pistons S onends of one stem, which carries in its center a helical rack J. Workingin rack J is a worm or enclless screw K on spindle K, having alsothereon hand-wheels K and K and a friction-wheel or driving-wheel K thecylinders I-l having sockets H at their back ends connected by the pipesF and F to crank-cylinders D, as before described, and they also arefilled with It is preferable, though not essential, in order to make upfor any possible leakage in the plungers or passages to use anintensifier (see Fig. 4) consisting of a cylinder L with inlet L andhaving therein a ram L and always communicating by pipe L with one orother of the pipes F and F. This ram is worked by pis ton M in cylinderM, whose end is in communication with the source of hydraulic power, sothat, cylinder L being kept filled with non-compressible fluid, leakage,if any, will be constantly replaced and the rams O in crank-cylinders Dkept effective in action.

Any motion given to the spindle K, either byhand-wheels K or K or by thegearingwheel K which is driven by some automatic regulating devicesactuated by the lift or by the spindle around which the load is hoisted,

is by worm K and rack J transmitted to the rams J and by means of theconnecting-pipes F and F, as before described, to the crankcylinders D,where, the rams 0 being actuated, the position of the crank O is alteredradially and its leverage made to suit the load to be lifted. Thus theamount of water consumed in and by the cylinders A, Figs. 1 and 2, ismade proportional to the load. Further, when the engine is used wherepower may be conserved, as where a load is lowering, it (the engine) isconverted into a pump drawing from the exhaust the amount of watercommensurate with the work of the falling load and forcing it back intothe accumulator or the pressure-main.

Referring to Figs. 5 and 6, the pump-cylinders a have plungers I)connected to crank c, which has ram extensions 0 in cylinders cl incrank-disk d. The ends of cylinders d are connected by pipes 61 d andpassages and ports throughshaft e, stationary annulus f, and pipes f fto the controlling or regulating devices similar to those described andshown in reference 'to the engine of Figs. 1 and 2. The motion of themotive powershaft is communicated to shaft e, and according to the forceexerted is the position of the crank-pin c in radial slot (Z adjusted,giving it more or less leverage and making the pump do more or lesswork. The motion may be communicated to the pump-shaft by belt or chain,or, say, preferably, f riction-gearin g, onto friction-pinion g.

A hydraulic compensating pump such as that shown in Figs. 5 and 6 in usewith a hydraulic multiplying lift would have (seeFig. 7) a tensiondevice at the end of the lift cylinders or ram H a friction or othergearing between the pulley-shaft and the pump-shaft, and a supply andexhaust valve worked by a tension device. The sheave-bracket h holds, aswell as sheaves j,an additional sheave,such as that markedj in Fig. 9,orasprocket-wheel or a friction-wheel in gearing with the shaft of thepump, say by means of pinion 9, (see Fig. 5,) so that such pump wouldwork according to the power communicated from said sheave-pulley orfriction-wheel. The adj ustability of the crank of the pump iscontrolled by the tension on the rope or chain of the lift. In thesheave-bracket h is the fulcrum 7t of lever is, fixed to end bolt of thefixed end j of hoisiin g-rope j This end bolt slides in bracket h andterminates under said supply port m so arranged that when port 191. isin through communication with it then m is in through communication withport m and when port m is in communication With it port m is incommunication with port m,

these ports m and m being exhaust-ports. The ports Z and Z of theauxiliary valve are connected up by pipe f 6 and ports Z Z by pipe f tothe through-passages of the crank-shaft of a compensating hydraulicpump, as before described, thence to the crank-pin rams or cylinders ofsame by pipes d d respectively that is, l and 1 connect to d and Z and Zto d".

The attendant regulates the controllingvalve m by moving spindle m up ordown, while the pull or tension on the rope j by compressing orslackening spring k moves lever 10 and regulates the auxiliary valve Lthe normal position of this latter valve L being shown in the drawings.Now in raising a heavy load the spring k would be compressed and leveris be moved upwardly by the tension on the rope, (see Fig. 16,)valvestem Z would move the valves thereon, and pressure enter theelevator ram cylinder through port mflthe port m being-the exhaustepassage from said ram-cylinder. Pressurewater would also pass to thecrank-pin cylinders through pipes and ports m m Z and f 6 d to the outercylinderd, Fig. 5, while the other or inner cylinder 01 would be open tothrough pipe (1 pipe f", the through passage of the shaft-pipe Z andports Z, m, and m. This causes the crank-pin to move inwardly untillever k resumes its normal position with supply out 01f to port I. Theamount of water pumped back into the accumulator or pressure-main istherefore increased or decreased by means of the tension on the rope,and by this means when the car is ascending with a partial load thewater which would be otherwise wasted is pumped back into main oraccumulator, as also if the car is descending the water equivalent tothe load is so returned to power reservoir.

Figs. 8 to 14 illustrate modifications of the regulating devices of ahydraulic compensating pump such as that shown in Fig. 5 when used inconnection with a multiplying hydraulic lift. In this case the tensiondevice is dispensed with and a speed-governor performs the function ofregulating. The cylinder or ram H has bracket h, carryingactuating-sheave j and additional frictionsheave j for working the pump.The controlling-valve m is worked by the attendant, while aspeed-governor worked by turbine N actuates auxiliary valve L similar tothat shown in Fig. 7, save that the ports Z and Z are dispensed with.Ports P and Z are exhaust-passages to waste-water tank,and a supply-portZ is made between the ports Z and 1 which latter are connected to pipesf and f respectively, of hydraulic compensating pump.

The operations of the mechanisms shown in Figs. 8 to 11 will be moreclearly -understood on reference to the details of the valve shown inFigs. 12, 13, and14. In raising a light load the spindle m of the valvem is moved upwardly, opening the port 1 to the pressure-water, whichpasses upwardly in cess of pressure over the load to be raised.

Flowing from the turbine, the water passes through pipe 7, havingbranches to both ports 8 and 11 of the valve, the former port 8 beingclosed through port 10 to the main ram or cylinder I-I The turbine N isat the same time revolving the governor-balls n, which lift and lower,as the case may be, the lever n and move spindle 1 of the auxiliaryvalve. \Vhen balls n fly outwardly, owing to increase of speed, thevalve-spindle is depressed and supply-port Z communicates through port Poipe f through passage in shaft 6, and pipe d to inner crank-pinramcylinder cl, while at the same time exhaust is open from the outercrank-cylinder d through pipes d through passage in shaft e, pipe f portl and exhaust-passage 2 to waste-water tank. This action moves rams Oand forces crank-pin c outwardly from the center of shaft 6, Fig. 5, andso increases the radial leverage or stroke of the pump, and thereforethe quantity of water per stroke which it draws from the waste-watertank and forces into the accumulator or back into the main,'whichquantity corresponds to the excess of power exerted over the loadlifted. hen the valve m has been (by the attendant) placed in itshighest possible position, as it'is required for elevating loads, thesupply-port l and port 9 freely communicate and a full volume ofpressure will pass to the main ram IP, as well as the pressure-supply,by way of the turbine N through port 1, passage 2, pipe 3, ports 4: and5, pipe 7, branch 8, port 11, and port 10.

In lowering a heavy load valve-spindle m is depressed and the water fromthe main ram H passes by way of passage 9, passage 2, port 3, pipe 4,and port 5 to the turbine N which it revolves similarly as beforedescribed with a velocity proportional to the excess of load over thenormal load. Extra speed depressin g the lever Z the pressure-water fromport lpasses, as before described, through port 1, pipe f and pipe d tothe inner crank ramcylinder and leaves the outer crank ram-cylinder openper exhaust-passage 1 to wastewater tank, thus causing the crank-pin cto move outwardly or increase its leverage, the

exhaust-water of the main ram leaving the turbine N per port 6, pipe 7,and port 8, (branch 11 being closed,) and port 12 to the waste-watertank. When valve M is in its lowermost position, as in lowering loads,the passage 9 is open to port 13 and the exhaust from the ram-cylinderpasses in volume to the waste-water tank.

From the foregoing descriptions and by the aid of the letters ofreference to which such descriptions refer and which are placed upon thediagrams, it will not be necessary to state anything further in relationto Figs. 15 to 22,

IIO

except to point out in general terms what each figure represents.hydraulic-lift-regulating devices and a hydraulic compensating pumpdriven from the gearing of said lift, and the arrangement is shown aswhen the mechanism is at restthat is, neither lifting or loweringa load.Fig. 16 isa diagram of similar gearing with the mechanism as it wouldappear when a heavy load was being elevated, and Fig. 17 is the samewhen a light load is being elevated. Fig. 18 is a diagram showing themechanism when a light load is being lowered, and Fig. 19 is the samewhen a heavy load is descending. Figs. 20, 21, and 22 are similardiagrams to the above with the modification of regulating devices inwhich a turbine and governor-balls take the place of a tension device,Fig. 20 showing the position of the mechanism when at rest, Fig. 21 thesame when a light load is being raised or a heavy load is being lowered,and Fig. 22 the same when a heavy load is being lifted or a light loadis being lowered.

Having now particularly described and explained the nature of our saidinvention and in what manner the same is to be performed,

' we declare that what we claim is- Fig. 15 is a diagram of a In ahydraulic compensating pump or engine, the combination of a shaft gearedfor the transmission of power and having on one end a crank-diskprovided with ram-cylinders and a radial slot communicating therewith,the said shaft and crank-disk having throughpassages communicating withthe ends of ARTHUR EDWARD CUTLER. REGINALD DONKIN.

' -Witnesses:

THOMAS JAMES WARD, MICHAEL JOSEPH OANDRICK.

